EP1851455B1

EP1851455B1 - Thrust bearing assembly

Info

Publication number: EP1851455B1
Application number: EP06735451A
Authority: EP
Inventors: Charles W. Shattuck; David R. Torlai; Richard F. Murphy
Original assignee: Koyo Bearings North America LLC
Current assignee: JTEKT Bearings North America LLC
Priority date: 2005-02-22
Filing date: 2006-02-17
Publication date: 2010-07-21
Anticipated expiration: 2026-02-17
Also published as: JP4906742B2; CA2858039A1; CA2598641A1; CN101142418A; JP2008531944A; US7845857B2; US20090041402A1; CA2598641C; ATE475025T1; US20110069923A1; EP1851455B8; DE602006015615D1; CA2858039C; WO2006091503A1; US8182157B2; EP1851455A1; KR101341275B1; KR20070112814A; CN100591936C

Abstract

A thrust bearing assembly generally includes a cage and a plurality of rolling elements. The cage has first and second cage halves with each cage half having a respective radial segment with a plurality of circumferentially spaced openings. Each opening has an opening perimeter. The cage halves are interconnected with portions of the radial segments circumferentially between the plurality of openings abutting along a given plane and the respective openings aligned to defined rolling element pockets. The rolling elements are positioned in the rolling element pockets such that a centerline of each rolling element lies in or in proximity to the given plane. A flange extends along at least a portion of each opening perimeter to retain the rolling elements within a respective one of the rolling element pockets.

Description

FIELD OF THE INVENTION

The present invention relates to a thrust bearing assembly and in particular to a needle roller thrust bearing assembly.

BACKGROUND OF THE INVENTION

Referring to Figs. 11 and 12, an example of a prior art needle roller thrust bearing 1 is shown. The bearing 1 includes a plurality of cylindrical rolling elements 2 arranged radially from a center of rotation. The rolling elements 2 are retained and guided by a bearing cage 3, which forms the primary structure of the bearing 1.
There are several types of construction currently used to produce metallic needle roller bearing cages 3. Figs. 13 and 14 show a thrust bearing 1A with a cage 3A that is constructed of two halves 4. Each half 4 has rectangular window openings 5 which are slightly smaller in width than the diameter of the rolling elements 2. Each cage half 4 also has circumferential flanges 6 which are directed inwardly towards the opposite member. When joined together, these two cage halves 4 form a box which provides structural integrity for the assembly, along with guidance for the rolling elements 2 and their retention in both directions.
A prior art thrust bearing 1B with a cage 3B having another construction is shown in Figs. 15 and 16. In this construction, the cage 3B is formed from a single piece of metal into a shape which, along with specially shaped openings, retains and guides the rolling elements 2. In cross-section, this type of cage 3B has a shape similar to that of the Greek letter sigma (E).
Another thrust bearing 1C having a cage 3C of yet another construction is shown in Figs. 17 and 18. Here, the cage 3C has a material thickness close to the diameter of the rolling elements 2 and has rectangular openings 5 to accept the rolling elements 2. Retention is provided by staking 7 or otherwise forming the cage face near the openings 5 so that these are made smaller than the diameter of the rolling element 2.
A further prior art thrust bearing assembly is known from publication FR 2 242 595 A . This known thrust bearing assembly comprises the features contained in the preamble of claim 1.

SUMMARY OF THE INVENTION

A thrust bearing assembly includes a cage and a plurality of rolling elements. The cage has first and second cage halves with each cage half having a respective radial segment with a plurality of circumferentially spaced openings. Each opening has an opening perimeter. The cage halves are interconnected with portions of the radial segments circumferentially between the plurality of openings abutting along a given plane and the respective openings aligned to define rolling element pockets. The rolling elements are positioned in the rolling element pockets such that a centerline of each rolling element lies in or in proximity to the given plane. A flange extends along at least a portion of each opening perimeter to retain the rolling elements within a respective one of the rolling element pockets. The thrust bearing assembly is characterized in that each flange is formed as a plurality of tabs, and tabs from one cage half alternate with tabs of the other cage half on at least a portion of a respective opening perimeter.

BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 1 is a partial isometric view of a needle roller thrust bearing assembly ;
Fig. 2 is a cross-sectional view along the line 2-2 in Fig. 1;
Fig. 3 is a cross-sectional view similar to Fig. 2 showing a thrust bearing assembly according to the invention;
Fig. 4 is an exploded view of a portion of the cage as indicated by the circle 4 in Fig. 1 with the rolling elements removed for clarity;
Fig. 5 is a cross-sectional view along the lines 5-5 in Fig. 1;
Figs. 6-8 are cross-sectional views similar to Fig. 5 illustrating other examples of a thrust bearing assembly;
Fig. 9 is a cross-sectional view illustrating the needle roller thrust bearing assembly of Fig. 1 positioned between a pair of bearing surfaces;
Fig. 10 is a cross-sectional view similar to Fig. 9 showing another example of a thrust bearing assembly;
Fig. 11 is a cross-sectional view along line 11-11 in Fig. 12;
Fig. 12 is a front elevation view of a prior art thrust bearing;
Fig. 13 is a partial cross-sectional view of an alternative prior art thrust bearing;
Fig. 14 is a partial isometric view of the cage of the thrust bearing of Fig. 13;
Fig. 15 is an isometric view of a cage of another prior art thrust bearing;
Fig. 16 is a partial cross-sectional view of the alternative thrust bearing using the cage of Fig. 15;
Fig. 17 is an isometric view of yet another alternative prior art thrust bearing;
Fig. 18 is a cross-sectional view along the line 18-18 in Fig. 17;
Fig. 19 is a cross-sectional view along the line 19-19 in Fig. 13; and
Fig. 20 is an exploded view of a portion of the cage as indicated by the circle 20 in Fig. 14.

DETAILED DESCRIPTION

The present invention will be described with reference to the accompanying drawing figures wherein like numbers represent like elements throughout. Certain terminology, for example, "top", "bottom", "right", "left", "front", "frontward", "forward", "back", "rear" and "rearward", is used in the following description for relative descriptive clarity only and is not intended to be limiting.
Referring to Figs. 1 and 2, a needle roller thrust bearing assembly 20 is shown. The thrust bearing assembly 20 includes a cage 22 supporting a plurality of preferably cylindrical rolling elements 2 arranged radially from a center of rotation (not shown). The cage 22 comprises two cage halves 24, 26. Each cage half 24, 26 includes a radially extending segment 25, 27 respectively with circumferentially spaced openings 30, 32 respectively. Each radially extending segment 25, 27 includes portions 47, 48 circumferentially between the plurality of openings 30, 32.
The openings 30, 32 are preferably generally rectangular and configured to receive the rolling elements 2. The cage halves 24, 26 are interconnected with the openings 30, 32 radially and circumferentially aligned and with at least portions such as portions 47, 48 of the radially extending segments 25, 27 abutting one another along a plane P. The centerline of each of the rolling elements 2 lies in or in proximity to the plane P. In this example, circumferential flanges 28 are provided at the inner and outer diameters of the radial portions 25, 27 to provide a piloting surface for the thrust bearing assembly 20 and to provide additional structural rigidity for the cage 22.
Each opening 30, 32 has a flange 34 about at least a portion of or the entire opening perimeter. Each flange 34 extends outwardly from the plane P. The flanges 34 are formed in such a way as to guide and retain the rolling elements 2. An advantage of this design over the prior art cage 3 constructions is that any portion of the cage 22 of the present example that contacts the rolling elements 2 has a smooth rolled and formed surface. In contradistinction, as shown in Fig. 19, the surfaces that contact the rolling elements 2 of the cage 3A are pierced such that the opening 5 is defined by rough pierced surfaces 10 which can interfere with proper lubrication and also lead to wear.
Fig. 2 illustrates how the configuration of the thrust bearing assembly 20 allows an effective lubricant film to be developed. Specifically, lubricant can be captured in the generally triangular area defined between the rolling element 2 and the two abutting cage halves 24, 26. The abutting portions 47 and 48 close off the triangular area between the flanges 34 and prevent the lubricant from escaping circumferentially from adjacent the rolling element 2. Lubricant that either splashes into or is carried by adhesion to the rolling element 2 into this generally triangular area will tend to accumulate in this area and help promote a hydrodynamic lubricant film between the rolling element 2 and the surfaces 35 of the flanges 34. The smooth, generally convex surfaces 35 of the flanges 34 will minimize the "scraping" of lubricant off the rolling element 2 and will help maintain the presence of lubricant in the generally triangular area adjacent the rolling element 2. The smooth surfaces 35 also minimize direct contact between the rolling elements 2 and the cage 22, thereby reducing friction and wear.
A form of the flange construction for rolling element openings 30, 32 according to the invention is shown in Fig. 3. In this case, the cage halves 24A, 26A still abut on the plane P extending along or approximately along the centerline of the rolling elements 2, however, the flanges 34A along the length of the rolling elements 2 are divided into separate tabs 37. These tabs 37 are formed to present a smooth, generally conforming surface to the rolling elements, which is a variation of the smooth, generally convex surfaces 35 shown in Fig. 2. However, the tabs 37 are directed towards the opposite side of the rolling elements 2 rather than the closest side. In order to secure retention of the rolling elements in both directions, the tabs 37 are arranged so as to alternate on a portion of the perimeter such as along the length of the rolling elements 2. This sturdier construction allows a greater length of flange 34A. This additional length allows for greater flexibility in the shape of the flange 34A and is particularly useful for bearing assembly 20 with rolling elements having smaller diameters and that have tighter space restrictions for the cage 22.
In addition to improved wear and lubrication, another advantage of the cage 22 of thrust bearing assembly 20 is the substantially greater strength it provides compared to existing types of cage construction. This is particularly important in those areas with high concentrations of stress, such as the corners of the cage openings. Figure 20 shows a portion of a prior art cage 3A, taken near the inner diameter. It can be seen that the corners 13 of the cage openings 5 must be at right angles and relatively sharp to clear the rolling elements. The trapezoidal shape of the cage bars 14 between the openings 5 exacerbates this situation in the prior art designs because there is minimal cage material to resist stresses caused by radial and torsional loads on the cage. Referring to Fig. 4, the flanges 34 of the thrust bearing assembly 20 includes a continuous surface at the corners 31 of the generally rectangular openings 30, 32. This structure can increase the cage strength in two ways. First, the flanges 34 provide additional material all around the openings 30 for the rolling elements 2. In the areas of high stress, such as corners 31 near the inner diameter, the flanges 34 can as much as double the amount of material available to resist these stresses. The cage openings 30 are further strengthened by the actual shape of the flanges 34. The flanges 34 are designed in such a way that the stresses are directed away from the corners 31 of the openings 30. The combination of additional material and optimized stress flow results in cage strength that is several times greater than that of the prior art constructions.
There are several possible ways to interconnect the two cage halves 24, 26 to form the rigid cage 22. Using the embodiment of the sealed bearing assembly 20 as shown in Figure 3, the rolling elements 3 can be snapped past the tabs 37 to join the cage halves 24A, 26A and form a unitary thrust bearing assembly 20.
Several additional examples of interconnecting the cage halves 24, 26 are shown in Figs. 5-8, however, other methods may also be utilized. Referring to Fig. 5, the cage halves 24, 26 are spot welded 40 at various points along the abutting radial portions 25 and 27. Fig. 6 illustrates a mechanical joint 42 created by partially piercing the radial portions 25, 27 and locking the two halves 24, 26 together. Referring to Fig. 7, a circumferential band 44 is secured to the inner and/or outer diameters of the cage halves 24, 26 about the inner or outer flanges 28 to secure the halves 24, 26 together. In the example shown in Fig. 8, one of the cage halves 26B does not have a flange, but instead terminates in the radial portion 27. The other cage half 24B has a flange 46 extending from the radial portion 25 that extends toward and wraps around the radial portion 27. While the flange 46 is illustrated as being along the cage outer diameter, it is also possible to provide the flange 46 along the cage inner diameter.
Another advantage is that various combinations of differently sized circumferential flanges 28 at the inner and outer diameter of the cage 22 can be used to control lubricant flow within the bearing assembly 20. In some cases it is desirable to restrict or partially restrict the lubrication flow, while in other cases it is desirable to allow as much flow as possible. For example, Fig. 9 shows the thrust bearing assembly 20 of Fig. 1 positioned between two structures 50 and 52. As can be seen, the inner and outer diameter circumferential flanges 28 restrict the radial oil flow past the bearing assembly 20. Fig. 10 shows another thrust bearing assembly 20C positioned between structures 50, 52. The thrust bearing assembly 20C includes a cage 22C with interconnected halves 24C and 26C. Both halves 24C and 26C are without flanges which thereby allows more oil flow past the bearing assembly 20C. Other designs could incorporate partial or shorter flanges 28 to partially restrict flow.
The present invention addresses the essential requirements of a thrust bearing cage, namely, structure, guidance and retention, in a manner than greatly improves both the strength, rigidity, lubrication advantages, and the efficiency of the bearing assembly. Further, a low profile of the bearing assembly can be achieved.
The invention is defined by the following claims.

Claims

A thrust bearing assembly (20, 20C) comprising:
a cage (22) having first and second cage halves (24A, 26A), each cage half having a respective radial segment (25, 27) with a plurality of circumferentially spaced openings (30, 32), each opening having an opening perimeter, the cage halves being interconnected with portions of the radial segments circumferentially between the plurality of openings abutting along a given plane (P) and the respective openings aligned to define rolling element pockets;

a plurality of rolling elements (2) positioned in the rolling element pockets such that a centerline of each rolling element lies in or in proximity to the given plane; and

a flange (34A) extending along at least a portion of each opening perimeter to retain the rolling elements within a respective one of the rolling element pockets;

characterized in that each flange is formed as a plurality of tabs (37), and tabs from one cage half alternate with tabs of the other cage half on at least a portion of a respective opening perimeter.
The thrust bearing assembly (20, 20C) of claim 1, wherein the centerline of each rolling element (2) lies in the given plane (P).
The thrust bearing assembly (20, 20C) of claim 1 or claim 2, wherein each flange (34A) extends along the entire perimeter of a respective opening (30, 32).
The thrust bearing assembly (20, 20C) of any of the preceding claims, wherein the openings (30, 32) are generally rectangular.
The thrust bearing assembly (20, 20C) of claim 4, wherein each flange (34A) includes a continuous surface at corners (31) of the generally rectangular openings (30, 32).
The thrust bearing assembly (20, 20C) of any of the preceding claims, wherein at least one cage half (24A, 26A) includes a flange (28) along an outer radius, the flange extending away from the given plane (P).
The thrust bearing assembly (20, 20C) of any of the preceding claims, wherein at least one cage half (24A, 26A) includes a flange (28) along an inner radius, the flange extending away from the given plane (P).
The thrust bearing assembly (20, 20C) of any of the preceding claims, wherein the cage halves (24A, 26A) are joined together by one of spot welding, a mechanical joint, a circumferentially extending clamping band, and a portion of one cage half overlapping and clamping a portion of the other cage half.
The thrust bearing assembly (20, 20C) of any of the preceding claims, wherein the cage halves (24A, 26A) are identical.
The thrust bearing assembly (20, 20C) of any of the preceding claims, wherein the flange (34A) includes a smooth curved surface adjacent the rolling element (2).